CN105822460A - Combustion gas feeding and ignition device for a gas engine - Google Patents

Combustion gas feeding and ignition device for a gas engine Download PDF

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Publication number
CN105822460A
CN105822460A CN201610141402.2A CN201610141402A CN105822460A CN 105822460 A CN105822460 A CN 105822460A CN 201610141402 A CN201610141402 A CN 201610141402A CN 105822460 A CN105822460 A CN 105822460A
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CN
China
Prior art keywords
valve
igniter
gas
plunger
gas supply
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Granted
Application number
CN201610141402.2A
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Chinese (zh)
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CN105822460B (en
Inventor
M·肯策尔
G·科格勒
P·施泰因吕克
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Hoerbiger Kompressortechnik Holding GmbH
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Hoerbiger Kompressortechnik Holding GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B19/00—Engines characterised by precombustion chambers
    • F02B19/10—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder
    • F02B19/1019—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber
    • F02B19/108—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber with fuel injection at least into pre-combustion chamber, i.e. injector mounted directly in the pre-combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B19/00—Engines characterised by precombustion chambers
    • F02B19/12—Engines characterised by precombustion chambers with positive ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B19/00—Engines characterised by precombustion chambers
    • F02B19/16—Chamber shapes or constructions not specific to sub-groups F02B19/02 - F02B19/10
    • F02B19/18—Transfer passages between chamber and cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B43/00—Engines characterised by operating on gaseous fuels; Plants including such engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0639—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels
    • F02D19/0642—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels at least one fuel being gaseous, the other fuels being gaseous or liquid at standard conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0245—High pressure fuel supply systems; Rails; Pumps; Arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0248—Injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0248—Injectors
    • F02M21/0251—Details of actuators therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0248—Injectors
    • F02M21/0257—Details of the valve closing elements, e.g. valve seats, stems or arrangement of flow passages
    • F02M21/026—Lift valves, i.e. stem operated valves
    • F02M21/0263—Inwardly opening single or multi nozzle valves, e.g. needle valves
    • F02M21/0266—Hollow stem valves; Piston valves; Stems having a spherical tip
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0248—Injectors
    • F02M21/0275—Injectors for in-cylinder direct injection, e.g. injector combined with spark plug
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0293—Safety devices; Fail-safe measures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/02—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 of valveless type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1813—Discharge orifices having different orientations with respect to valve member direction of movement, e.g. orientations being such that fuel jets emerging from discharge orifices collide with each other
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/30—Use of alternative fuels, e.g. biofuels

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

For a fuel gas feed and Ignition apparatus for a gas engine (1) with a combustion chamber injection nozzle (12) in which a number of injection channels (37) are provided for a main fuel gas, and the injection channels (37) are connected to a main fuel gas feed line (24) for main fuel gas in which a main fuel gas valve (21) is arranged, and in which combustion chamber injection nozzle (12) are also provided a number of torch channels (52) for hot combustion gas and the torch channels (52) are connected to a pre-combustion chamber (15) in the fuel gas feed and ignition apparatus (10), wherein an ignition fuel supply line (17) leads to the pre-combustion chamber (15) and a pre-combustion chamber valve (18) is arranged in the ignition fuel supply line (17), control of both the time and the duration and thus also the quantity of the injection of main fuel gas, as well as of Ignition fuel for the pre-combustion chamber completely independently of one another and in a precise and, above all, rapid manner is achieved in that both the main fuel gas valve (21) and the pre-combustion chamber valve (18) are embodied as an electrically actuated, electronically controlled valve.

Description

The gas supply of gas engine and igniter
Technical field
nullThe present invention relates to a kind of gas supply for gas engine and igniter，Described gas engine has combustion chamber burner，Some injection channels for main combustion gas are set in described combustion chamber burner，And injection channel is connected with the main gaspipe for main combustion gas，Some passage of flames for the burning gases of heat are set in combustion chamber burner，And passage of flame is connected with the precombustion chamber in gas supply and igniter，Igniter fuel supply pipe is passed in precombustion chamber，And in igniter fuel supply pipe, it is provided with prechamber valve，Described prechamber valve is configured to electrically operated、Electronically controlled valve. in addition，The invention still further relates to a kind of method for running gas engine，In the process，During compression stroke in the cylinder of gas engine compressed air or air/exhaust-gas mixture，And the air of compression is pressed in precombustion chamber，Igniter fuel is sent in precombustion chamber for forming air/igniter fuel mixture，Before compression stroke terminates, main combustion gas is sent in the main combustion chamber of cylinder，And the air in precombustion chamber/igniter fuel mixture is lighted，Thus the burning gases of heat are flowed into main combustion chamber from precombustion chamber，And there the main combustion gas sprayed into is lighted.
According to meaning of the present invention, described gas engine refers to have piston, the internal combustion engine especially with reciprocating piston that is piston-mode motor.
Background technology
nullThe known combustion method of external source igniting gas engine is based on following principle: or during filling cylinder in the intake stroke, flammable mixture is supplied to working chamber，In working chamber, flammable mixture is formed by spraying into combustion gas during compression stroke. then light flammable mixture by spark ignition or by the way of spraying into a small amount of pyrophorisity liquid fuel. here when lighting when，Fuel for combustion mixes with combustion air. can light the most in the cylinder，Or indirectly light by the way of lighting in precombustion chamber. can be lighted in precombustion chamber by spark ignition mode，This will cause and is discharged to the hot gas jet main combustion chamber (cylinder) from precombustion chamber，Described hot gas jet makes the flammable mixture in main combustion chamber light，Generally turbulent flame forward is then across flammable mixture. raised by igniting in main combustion chamber and the pressure so realized，Required mechanical useful work is completed by piston in power stroke. these the most effective and the most sane combustion methods have shortcoming: all have cutoff or advanced ignition tendency when fuel air ratio is disadvantageous，It may result in the highest discharge of poisonous waste、The efficiency of difference and/or extreme mechanical load. this type of cutoff or advanced ignition all can threaten the secure and reliable operation of gas engine. and quick load change is particularly likely to cause the above-mentioned undesirable change of fuel air ratio. thus when to the requirement height of load variations speed，The use of gas engine will be restricted.
nullSuch as US8,800,529B2 discloses a kind of solution that can overcome this shortcoming，Which describe a kind of combustion method sucking air，Suck air in the intake stroke，Compressed air in compression stroke，And before piston soon arrives top dead centre，Just spray into main combustion gas by jet rose，The process spraying into diesel oil with compression ignition diesel engine is similar. owing to gas has the highest autoignition temperature，Therefore by so-called control injection, main combustion gas is lighted，When controlling injection, a small amount of pyrophorisity liquid fuel is injected in main combustion chamber. then，The diffusion combustion that the burning of main combustion gas will act as carrying out along main jet-flow surface is carried out. knownly，The required oxygen that makes to burn is diffused in flame via flame fringe，Can be carried out diffusion combustion，Without being pre-mixed air and fuel. flame directly " sucks " oxygen from the environment of next-door neighbour and burns. therefore，The oxygen supplied to flame towards flame core is fewer and feweri，But and fuel only part burning in flame core. due to this combustion method only compressed air，Therefore there is no the danger of advanced ignition. by liquid fuel control injection time can highly reliably spontaneous combustion and prevent cutoff.
From the known a kind of injection valve for this combustion method of EP520659A1 and EP778410A1, also referred to as double fuel valve. it is concentrically disposed with in injection valve for spray combustion week fuel gas and each valve controlling to spray the liquid fuel lighted a fire.
The major defect of this combustion method is must provide for two kinds of fuel, namely as the gases at high pressure of main combustion gas with for controlling the diesel oil of injection, and is set to this required double fuel bin and feedway.
US2, 799, 255A describes the gas engine of a kind of external source igniting sucking air, described gas engine uses natural gas and works according to diffusion combustion method. in order to gas engine safely and reliably can be lighted a fire in all load ranges, wherein avoid cutoff and advanced ignition, it is provided with the precombustion chamber being connected by flow channel with the main combustion chamber in cylinder chamber or cylinder. the air in compression cylinder during compressing, compressed air is sent in precombustion chamber simultaneously. under stress fuel is sent in precombustion chamber, fuel mixes in precombustion chamber with compressed air. should so determine fuel and the mixed proportion of air in precombustion chamber, make the fuel/air mixture will not Self-lighting.Before compression stroke terminates, gaseous state main fuel is sent in main combustion chamber by the amount needed for corresponding load.Then before compression stroke soon terminates, by spark plug, the fuel/air mixture in precombustion chamber to be lighted. the burning gases of heat are flowed in main combustion chamber via flow channel. gaseous state main fuel flow is directed at this air-flow, so that main fuel and compressed air turbulent closure scheme, and thus light main fuel/air mixture.Main fuel/air mixture burns along flame front with the form of diffusion combustion method.
nullAt US2,799,255A controls to be sent to fuel be sent in main combustion chamber in precombustion chamber and by main fuel with mechanical forced control mode by cam drive mechanism. again，Camshaft control crank，Described crank acts on the valve tappet of fuel valve and main fuel valve，Wherein，Valve tappet is also by crank forced synchronism. determine the supply of fuel or main fuel with this，If but produced fuel/air mixture and main fuel/air mixture are same. cannot reliably prevent the spontaneous combustion caused due to compression heating. the cutoff caused due to mixture excessive rarefied in precombustion chamber cannot be stopped equally. the fuel of delivery quality change or main fuel，Then it is particularly likely to be problem，The natural fuel of such as natural gas is entirely possible this situation. at US2,799,The mode improving this situation in 255A is only that the pressure changing fuel and/or main fuel is to realize required coupling. due to pressure controlled built-in inertia，Possibly injection cannot be followed the tracks of with sufficiently fast speed during load Rapid Variable Design，The most especially when load Rapid Variable Design it cannot be guaranteed that reliable ignition.
But DE102014000229A1 also illustrates a kind of gas engine utilizing diffusion combustion method. can only pass through the main fuel quantity that needle valve element controls to burn in main combustion chamber indirectly wherein, control valve is in needle valve element described in the low-pressure side upper-pilot of needle valve element. therefore it is more difficult to control the burning in the emitted dose of main combustion gas and main combustion chamber.
Summary of the invention
In order to solve problem of the prior art, according to the present invention, on the one hand regulation, arranges main gas valve in main gaspipe, described main gas valve is configured to valve electrically operated, electronically controlled, and main gas valve is also configured in addition to prechamber valve valve electrically operated, electronically controlled.On the one hand this can realize, and the most accurately and the most promptly controls main combustion gas and the time for spraying of igniter fuel, injection duration and emitted dose for precombustion chamber.With this, on the one hand the variation characteristic of main combustion gas and/or igniter fuel can be reacted rapidly, and on the other hand with this, injection can also be matched with different load conditions. this most also can realize ensureing reliable ignition when load changes rapidly and optimizing burning.Gas supply of the present invention and igniter cannot be only used for four stroke gas engines, and can also be used for two-stroke gas electromotor.
But by use electrically operated, electronically controlled valve can also realize a kind of particularly advantageous ignition method. again, can be before the air in lighting precombustion chamber/igniter fuel mixture, again igniter fuel is sent in precombustion chamber, so that the air in enriching (auffetten) precombustion chamber/igniter fuel mixture. by described multiple injection, utilize first time to be injected in precombustion chamber and produce air/igniter fuel mixture the thinnest, that certainly will not light voluntarily.Just spray enriching air/igniter fuel mixture by second time in the moment of desired igniting and carry out external source igniting.In addition, sprayed by second time and also reduce the temperature of air/igniter fuel mixture in precombustion chamber, thus the danger of undesirable advanced ignition can be reduced further. advanced ignition and cutoff can be prevented as far as possible with this.
On the other hand according to the present invention, mechanical differential pressure is set between main gaspipe and injection channel and handles valve, this differential pressure is handled valve and is controlled by main gaseous-pressure and can close or block injection channel. therefore, on the one hand can reach to be partially disposed at main gas valve away from the high region of thermic load. on the other hand also can realize closely constructing gas supply and igniter, described gas supply and igniter can be arranged in the cylinder cover region that valve is located at. the most therefore can reduce produced main combustion gas dead band, the most also the discharge of poisonous waste of gas engine can be reduced, and the space that may pollute is little.
If being distributed the passage of flame of multiple burning gases for heat on the periphery of combustion chamber burner, these passage of flames are connected with precombustion chamber, then on the one hand it is capable of gas supply and igniter structural form closely, on the other hand a large amount of diffusion flame is thus lighted, these diffusion flames can optimally suck the oxygen that the burning being available in main combustion chamber uses, thus occur stable, good guiding and burn rapidly. thus can improve burning quality and efficiency, and the discharge of poisonous waste of gas engine can be reduced.
Particularly advantageously, injection channel and passage of flame circumferentially direction is alternately arranged side by side. can circumferentially be flowed in main combustion chamber in star with staggering in direction with the burning gases that this produces main combustion gas and heat, it is possible to realize reliable ignition and in main combustion chamber, realize the best diffusion flame spatial distribution. can also improve in the following way, that is, the entrance area that injection channel and passage of flame enter into main combustion chamber is substantially provided in the same axial position of combustion chamber burner.
By by the radially aligned main combustion chamber of entrance area of injection channel and passage of flame, it is achieved the burning gases of main combustion gas and heat are the most unhinderedly flowed in main combustion chamber, stable and the most controlled burning so can be improved further.
If ring-shaped pre-combustion chamber's groove is arranged in gas supply and igniter, described ring-shaped pre-combustion chamber groove is connected with precombustion chamber by precombustion chamber pipeline, and passage of flame is passed in described ring-shaped pre-combustion chamber groove, can be achieved with implementing gas supply and igniter particularly compactly.
Preferably mechanical valve is configured to valve tappet, described valve tappet has the first plunger on an axial end portion, and there is second plunger axially spaced with the first plunger, wherein, described first plunger is connected by bar and the second plunger, and is formed between the first and second plungers and the control chamber of main fuel gas supply conduit connection. realize, with this, the differential plunger that controlled by actuating pressure. such that it is able to mechanical valve is used in different gas engines in the case of geometric shape holding is constant.
For this in order to realize the embodiment in simple structure, plunger seal face preferably can be set on the first plunger, this plunger seal face sealingly engages effect with the valve sealing surface in gas supply and igniter, and the second plunger is arranged in the control recess of gas supply and igniter, wherein, the side face of the second plunger and with controlling concave seal mating reaction.
In order to can be by the movement limit of valve tappet in required degree, the second plunger is preferably axially adjoined with the latch of the counter stopper effect in gas supply and igniter. the most also closure speed can be kept as low with this, because need to be through stroke necessary to function for this.
If arranging spring around latch between backstop and the second plunger, then spring just can support closing motion, and also can realize the definition position of mechanical valve.
According to a kind of favourable embodiment, the second plunger is arranged in valve chest, and constituting in valve chest has valve backstop, the end face seal ground mating reaction of described valve backstop and the second plunger.Thus on the one hand can reduce the main gas leakage due to mechanical valve, and on the other hand mechanical valve can be configured to the plug-in unit that can provide for simple replacement of.
The valve spring between the end face and the valve chest that are arranged on the second plunger can be utilized again to support closing motion, and also can realize the definition position of mechanical valve.
Based on the enthusiasm condition in gas supply and igniter, advantageously it may be that a number of potted component is arranged on the side face of the second plunger. potted component can be matched with thermic load. main combustion gas excessive leakage is effectively suppressed in addition also by potted component.
In order to derive the main combustion gas of leakage, it can be stated that controlling deviating from control chamber and passing through to be passed through blow-by tube in the end that the second plunger is closed of recess.
In a kind of particularly advantageous embodiment, it can be stated that blow-by tube is connected with igniter fuel supply pipe. using, with this, the main combustion gas that may leak in precombustion chamber, this improves the efficiency of gas engine.It is particularly advantageous that completely at this and is, the same medium being simply placed in different pressures level if desired is used for the igniter fuel of main combustion gas and precombustion chamber. in addition, advantageously need not the blow-by tube derived from gas engine at this.
Accompanying drawing explanation
Being explained in detail below with reference to Fig. 1 to the 10 couple of present invention, these accompanying drawings are exemplary, schematically and without limitation illustrate the favourable embodiment of the present invention. in figure:
Fig. 1 illustrates the gas supply according to the present invention and the view of igniter,
Fig. 2 illustrates the gas supply according to the present invention and the sectional view of igniter,
Fig. 3,4,6,7 and 9 illustrate the sectional view of the details of the gas supply according to the present invention and igniter,
Fig. 5 illustrates the valve tappet of the mechanical valve of the gas supply according to the present invention and igniter,
Fig. 8 illustrates the cross section of combustion chamber burner, and
Figure 10 illustrates the gas supply according to the present invention and igniter and joint and control device.
Detailed description of the invention
Fig. 1 illustrates that the local of gas engine 1, described gas engine include that cylinder block 2 and the cylinder head 3 being diagrammatically only by are arranged in cylinder block 2 with valve 4. cylinder 5, and piston 6 can move back and forth in the cylinder.This Basic Design 26S Proteasome Structure and Function of internal-combustion piston engine is the most known, the most here it will not go into details. in cylinder head 3, it is additionally provided with the gas supply according to the present invention and igniter 10, main combustion gas utilizes described gas supply and igniter to be fed in the main combustion chamber 11 of cylinder 5, and utilize the ignition in main combustion chamber 11 of described gas supply and igniter, below will be described in more detail.
Fig. 2 illustrates cylinder 5 and gas supply and fire device 10 and the amplification view of critical piece thereof. gas supply and igniter 10 are so arranged in cylinder head 3, described gas supply and igniter are extend in main combustion chamber 11 with combustion chamber burner 12, described main combustion chamber is formed basically by free space between piston 6 and cylinder head 3 in cylinder 5. combustion chamber burner 12 is arranged on the axial end portion of gas supply and igniter 10. combustion chamber burner 12 is arranged on the stage casing 13 of gas supply and igniter 10, this stage casing is arranged on again on the epimere 14 of gas supply and igniter 10. it is also provided with on epimere 14 shown in Figure 10 for igniter fuel, main combustion gas, control piper, the joint of supply of electric power etc., hereinafter also this will be described in more detail.
Yes in the division of combustion chamber burner 12, stage casing 13 and epimere 14 arbitrarily. and gas supply described here and igniter 10 are a kind of gas supply that can favorably manufacture and igniter 10. from the point of view of production technology angle
In gas supply and igniter 10, in stage casing 13, it is provided with precombustion chamber 15 here, this precombustion chamber is essentially shaped as the recess in stage casing 13. and external source igniter 16 is passed in precombustion chamber 15, described external source igniter for example, spark discharge type spark plug, corona spark plug, plasma spark plug, laser-ignition unit etc.
Igniter fuel supply pipe 17 for the igniter fuel of precombustion chamber 15 is also passed in precombustion chamber 15 equally, shown in Fig. 3 shown as another kind of cutting trend, prechamber valve 18 is arranged in described precombustion chamber. for this prechamber valve 18 it is so structured that electrically operated, electronically controlled prechamber valve 18, such as the electromagnetic valve of gas-phase ignition fuel, and can be disposed in epimere 14. the nozzle 19 of prechamber valve 18 is passed in igniter fuel room 20 in an illustrated embodiment, this igniter fuel room is transitioned in igniter fuel supply pipe 17. as indicated by the arrows in fig. 3, by prechamber valve 18, igniter fuel can be sent in precombustion chamber 15 via igniter fuel supply pipe 17.
A preferred electrically operated, electronically controlled main gas valve 21 it is additionally provided with in epimere 14, its nozzle 22 is passed in main fuel chamber 23 (Fig. 2). and main fuel chamber 23 is transitioned in main gaspipe 24, by main gaspipe, main combustion gas can be sent in combustion chamber burner 12. in general, main gas valve 21 is arranged in main gaspipe 24, and controls in main gas supply to main combustion chamber 11.
According to described Advantageous embodiments, being also provided with a mechanical type pressure reduction and handle valve 25 in gas supply and igniter 10, in stage casing 13 and part is in combustion chamber burner 12 for part here. describe mechanical valve 25. in detail referring now to Fig. 4 to 6
Mechanical type pressure reduction is handled valve 25 and is made up of the valve tappet 30 of differential plunger form. and the diameter D2 that the first plunger 31 that valve tappet 30 includes on the axial end portion of valve tappet 30 and the second in axial direction spaced apart with the first plunger 31 plunger 32. first plunger 31 and the second plunger 32 pass through diameter D1 and the second plunger that bar 33 is connected with each other to constitute valve tappet 30. first plunger 31 is all higher than the diameter D3 of bar 33, thus starts form the first plunger surface A1 on the first plunger 31 and form the second plunger surface A2 on the second plunger 32 from bar 33.The latch 34 of the second axial end portion constituting valve tappet 30 can be adjacent to the second plunger 32. vertically and can be arranged on the outer peripheral face of the second plunger 32 by potted component 35.
Combustion chamber burner 12 is arranged the most through, here it is the valve recess 40 of blind hole form, end composition and the affiliated plunger seal face 36 on the first plunger 31 that it is axially closed sealingly engage the valve sealing surface 41 (Fig. 6) of effect. in order to constitute valve, valve tappet 30 is arranged in valve recess 40 with the first plunger 31 with its first axial end portion. in an illustrated embodiment, the free end face of the first plunger 31 is provided with plunger seal face 36, and constitute valve sealing surface 41. at this by the axial end portion of valve recess 40, first plunger 31 is radially spaced with valve recess 40, so that winner's burning gases can flow about and along the first plunger 31.The geometry in valve sealing surface 41 and plunger seal face 36 is inessential.
The closed axial end portion of valve recess 40 is connected with the outer peripheral face 47 of combustion chamber burner by the through injection channel 37 of the multiple radial directed in combustion chamber burner 12, the most also it is connected with main combustion chamber 11, wherein, first plunger 31 stops (above Fig. 6) according to the position of valve tappet 30 or release (below Fig. 6) main combustion gas flow to injection channel 37. here, injection channel 37 is distributed on the periphery of combustion chamber burner 12 preferably by opening regular spacing. and realize main combustion gas by the radial directed of injection channel 37 and radially flow in main combustion chamber 11.
If desired, injection channel 37 can also have slight tangent line orientation, in order to additionally realizes tangential inflow component.
The most through axial control recess 42 it is provided with in stage casing 13, this control recess is arranged coaxial and its immediately with valve recess 40. and the second axial end portion is arranged in control recess 42 with the second plunger 32 of valve tappet 30. and seal the side face of the second plunger 32 relative to control recess 42, the such as potted component 35 by means of the sealing ring form of the piston ring being similar to internal combustion engine seals.
Valve tappet 30 can be arranged on valve recess 40 and control in recess 42 with in axial direction moving.Baffle ring 44 can also be arranged on if desired in control recess 42 by the axial closing end composition controlling recess 42 for the backstop 43. of valve tappet 30, so as to adjust the position of backstop 43. between backstop 43 and the end face 55 of the second plunger 32, valve spring 45 is arranged around latch 34 ground, and the plunger seal face 36 of valve tappet 30 or the first plunger 31 is pressed against in the position of definition by valve spring towards valve sealing surface 41.
Main gaspipe 24 is passed in control chamber 46, described control chamber is formed between the first plunger 31 and the second plunger 32 by valve recess 40 and control recess 42 in gas supply and igniter 10. and the diameter D1 of the first plunger 31 is less than the diameter D2 of the second plunger 32, thus the first plunger surface A1 is less than the second plunger surface A2.nullFlow around the first plunger 31 and after the entrance region (until the region in plunger seal face 36) of the end face towards main combustion chamber 11 that therefore exists in the first plunger 31 in main combustion gas，Geometry according to valve tappet 30 and position，If the first plunger 31 partly or completely carries out pressure balance in view of the pressure of main combustion gas. it is fed under stress control in chamber 46 by main combustion gas now by main gas valve 21 and main gaspipe 24，Just produce valve action power due to plunger surface A2 bigger on the second plunger 32，This valve action power overcomes the pressure of the effect in valve recess 42 or spring cavity 38、And make valve tappet 30 be pressed against backstop 43. so the plunger seal face 36 of the first plunger 31 naturally also can be made to be lifted away from valve sealing surface 41 (below Fig. 6) if any also overcoming the pretightning force of spring if spring 35，Thus discharge injection channel 37，The main combustion gas being under pressure can be flowed in main combustion chamber 11.
When the rapid pressure drop re-closing main gas valve 21, thus controlling in chamber 46, pressure and/or spring 35 in spring cavity 38 make valve tappet be pressed against valve sealing surface 41 the most again, main combustion gas is thus stoped to be injected in main combustion chamber 11. the beginning of injection can not only be controlled by main gas valve 21 electrically operated, electronically controlled in a very simple way, and such as can be controlled the emitted dose of main combustion gas according to the current pressure of main combustion gas by the end of injection.
Due to the high-temperature in the required high pressure of main combustion gas and main combustion chamber 11 region, elastomeric seal the most generally cannot be used as the potted component 35 in the second plunger 32.If using and being similar to the sealing ring of piston ring as potted component 35, then there is main gas leakage in the inevitable side face along the second plunger 32. therefore in a kind of favourable embodiment, blow-by tube 39 is passed in spring cavity 38, and described spring cavity is formed in and controls in recess 42 between the second plunger 32 and backstop 43. and can plunger 32 and control between recess 42 the main combustion gas of leakage to derive by this blow-by tube 39.
If using same medium, such as natural gas as igniter fuel and main combustion gas, can be achieved with a kind of particularly advantageous embodiment. will leak out pipe 39 for this with lead to precombustion chamber 15 the igniter fuel supply pipe of prechamber valve 18 be connected (representing in Fig. 10). when injecting main combustion gas, the gas leakage occurred at this is guided prechamber valve 18 into via blow-by tube 39 and consumes there, if from without there is main gas losses. re-close main gas valve 21 after injection it, control the pressure in chamber 46 and decline the most rapidly.nullBut after blow-by tube 39 is connected with the igniter fuel supply pipe being under pressure，Second plunger 32 is used for the pressure of the igniter fuel of precombustion chamber 15 towards existence on the plunger surface A3 of spring cavity 38，Thus produce the closing force attempting making valve tappet 30 be pressed against valve sealing surface 41. on the one hand produce because of the differential pressure acted between spring cavity 38 and control chamber 46、On the other hand the counteracting force caused by pressure in main combustion chamber 11 a part of free end face of the first plunger 31 (this pressure act on also by injection channel 37) can resist this closing force. and once produced closing force is more than counteracting force，Allow for mechanical valve 25 to close. if there is valve spring 45，So valve spring will support closing force. but can also valve spring 45 be designed to the most weak，Make the most only to ensure the definition position of valve tappet 30.But valve spring 45 can also be abandoned in this embodiment completely, because by making mechanical valve 25 close for the pressure of the igniter fuel of precombustion chamber 15, and turned on by the pressure of main combustion gas.
It is of course possible to make the geometric match of valve tappet 30 and valve spring 35 in igniter fuel and the pressure of main combustion gas, normal to ensure that mechanical type pressure reduction handles the function of valve 25.
Above-mentioned embodiment allows to implement mechanical valve 25 the most compactly, and especially allows also to spatially separate with main gas valve 21. and with this, equally by main gas valve 21, spatially the high heat load parts near main combustion chamber 11 separate with gas supply and igniter 10.The another advantage of this embodiment can be seen that and is, dead volume in gas supply and igniter 10 is essentially limited to injection channel 37, and therefore can it be reduced to minimum as far as possible, this is particularly advantageous in being avoided or reduce soot and is formed or unburned exhaust gas constituents.The most thus can be to implement whole gas supply and igniter 10 the most compactly, this can realize being installed in the water cooling cylinder of gas engine 1, thus can realize the long-life and implement reliably.
In gas supply and igniter 10, here it is on the end face towards combustion chamber burner 12 in stage casing 13, it is also provided with the precombustion chamber groove 50 of annular, but this precombustion chamber groove is connected with precombustion chamber 15 by precombustion chamber pipeline 51. equally precombustion chamber groove 50 is arranged in combustion chamber burner 12.In combustion chamber burner 12, a number of passage of flame 52 is distributed in the periphery Shangdi of combustion chamber burner 12 and arranges, on the one hand these passage of flames are connected with the outer peripheral face 47 of combustion chamber burner 12, and the most also it is connected with main combustion chamber 11, and on the other hand it being passed into as shown in the sectional view in Fig. 7 in the precombustion chamber groove 50 of annular. precombustion chamber 15 is connected with main combustion chamber 11 by passage of flame 52 by precombustion chamber groove 50 and precombustion chamber pipeline 51. and passage of flame 52 is preferably implemented at this and is passed through the entrance area of main combustion chamber 11, make substantially radially to be flowed into main combustion chamber 11 from passage of flame 52, wherein, tangential inflow component can be set the most again.
Preferably, on identical axial location, passage of flame 52 is separately positioned between two injection channels 37 that circumferentially direction is adjacent, but such as can also be separately positioned on above or below injection channel 37 in the case of the dislocation not having circumferentially direction.It is conceivable that, also these arrangements of combination in any. advantageously injection channel 37 and the spatial distribution as well as possible of passage of flame 52, so as to constitute the most well distributed diffusion flame in main combustion chamber 11. particularly advantageously, injection channel 37 with passage of flame 52 the most substantially on identical axial location and the most circumferentially direction be the most alternately disposed adjacently, the most as shown in Figure 8.
Fig. 9 is utilized to describe again a kind of alternative embodiment of mechanical valve 25. differ primarily in that: mechanical type pressure reduction is handled valve 25 and had valve chest 53, valve spring 45 and the second plunger 32 are arranged in this valve chest. and the most also lack latch 34. and be provided with spring backstop 54 on first axial end portion of valve tappet 30 in deviating from of valve chest 53, here being the spring backstop of radially stepped form, valve spring 45 axially abuts in this spring backstop with one end.Valve spring 45 abuts on the free end face 55 of the second plunger 32 with the other end. and can also be as shown in Figure 9 for this, it being also provided with a recess in the end face 55 for being felt relieved by valve spring 45. valve spring 45 applies the most again spring force along the closing direction of mechanical valve 25, valve tappet 30 is pressed against valve sealing surface 41 by described spring force, and the most also ensures the definition position of valve tappet 30. but can also valve spring 45 discarded as described above.Arranging a valve backstop 56 in valve chest 53, be radial direction stepped form here, described radial direction step constitutes the backstop 43 of mechanical valve 25.A baffle ring 44 radially can also be reclined in this embodiment and be arranged in valve backstop 56, so as to adjust the position of backstop 43.In this case, the key advantage constituting this embodiment of valve backstop 56. be can be seen that and is by baffle ring 44, second plunger 32 abuts in (shown in Fig. 9) in valve backstop 56 in the open position of mechanical valve 25 with its end face 55, realize reliably sealing relative to the main combustion gas controlled in chamber 46 under high pressure by this valve backstop. when supplying main combustion gas under by the main gaspipe 24 high pressure in controlling chamber 46, this pressure acts on the valve surface A2 of the second plunger 32, and overcome spring force and the pressure acted in spring cavity 38 to make valve tappet 30 be lifted away from valve sealing surface 41, until the end face 55 of the second plunger 32 axially abuts in valve backstop 56. thus there will be no main gas leakage in spring cavity 38, the leakage of main combustion gas can be reduced with this.Otherwise potted component 35 will again undertake with the above as sealing function.
Valve chest 53 also can realize making material (dynamic load that impacts due to the method in backstop, thermal expansion etc. and processing (surface, coating, operation characteristic etc.) are matched with the requirement of mechanical valve 25, that is unrelated with the detailed description of the invention of gas supply and igniter 10.
Therefore mechanical valve 25 can also be fabricated to removable plug-in unit, described plug-in unit can be provided for simple replacement of in case of wear, since the abrasion that gas supply and igniter 10 cause not over mechanical valve 25 in this embodiment. such as valve chest 53 is such as arranged in control recess 42 for this, preferably arranged by press-fit manner, the most firm to ensure, and ensure valve chest 53 and control there is sufficient sealing function between recess 42.
Second axial end portion 57 of valve chest 53 can also appropriate variations, in order to be formed in the case of not having locking member and valve tappet 30 is maintained at the shoulder in valve chest 53. such as can manufacture shoulder simply by crimping mode.
nullIn a kind of embodiment of gas supply and igniter 10，Igniter fuel for precombustion chamber 15 is identical with the medium for main combustion gas，And there is the blow-by tube 39 being connected with igniter fuel supply pipe，Potted component 35. can also be abandoned during mechanical valve 25 closes in another embodiment，Control chamber 46 and include the pressure relevant with the combustion pressure in main combustion chamber 11. owing to diameter tolerance is inevitable，Little gap will necessarily be produced between second plunger 32 and control recess 42. therefore under the closure state of mechanical valve 25，Pressure balance can be realized between blow-by tube 39 and main gaspipe 24 by this little gap. thus can set up defined in mechanical valve 25 in injection start time、Recursive state. this pressure balance is thereby ensure that the stability of higher circulation，And with inject main combustion gas when mechanical valve 25 closes at the end of combustion pressure in main chamber 11 unrelated，And it is unrelated with the current loads of gas engine 1.
Gas supply according to the present invention explained below and the preferred function of igniter 10.
nullAir or () air/exhaust-gas mixture are flowed in cylinder 5 during induction stroke in the case of waste gas recirculation equally. in compression stroke subsequently, air compressed，By compressed air from cylinder 5 via passage of flame 52、Precombustion chamber groove 50 and precombustion chamber pipeline 51 are pressed in precombustion chamber 15. by prechamber valve 18, desired amount of igniter fuel be injected in precombustion chamber 15. and the igniter fuel sprayed into mixes with the compressed air being located therein in precombustion chamber 15. and use fuel gas as the igniter fuel for precombustion chamber 15，It being preferably used as the same medium that main combustion gas uses. the pressure of igniter fuel certainly have to be larger than the actuating pressure in precombustion chamber 15 at this. spray into igniter fuel with so measuring by prechamber valve 18，Make the thin igniter fuel/air mixture produced in precombustion chamber 15 that the advanced ignition of undesirable will not occur certainly.nullSuch as can be measured according to current load condition and igniter fuel characteristic by engine control system. utilize external source igniter 16 to be lighted by the igniter fuel/air mixture in precombustion chamber 15 at correct time of ignition (generally before the top dead centre of plunger 6). therefore it is the gas engine of a kind of external source igniting according to the gas engine 1 of the present invention. in being conducive to the period optimizing burning，Main combustion gas is injected in main combustion chamber 11 via injection channel 37 by main gas valve 21 with the above. owing to injection channel 37 distribution is arranged on periphery，Main combustion gas is radially injected in main combustion chamber 11 in star，As in Fig. 8 by main jet-flow 60 represented by as. in precombustion chamber 15, igniter fuel/air mixture is lighted，The burning gases of heat flow out from passage of flame 52.Owing to passage of flame 52 is arranged with being distributed on periphery, the burning gases of heat are in the most radially entering in main combustion chamber 11, as pass through represented by combustion gas jet 61 in Fig. 8.The pure main jet-flow 60 injected contacts with hot combustion gas jet 61 in main combustion chamber 11, thus the main combustion gas in main combustion chamber 11 is lighted, and constitutes the diffusion flame of a large amount of spatial distribution in main combustion chamber 11.Diffusion flame immediately wicks into operational oxygen, thus realizes stablizing, well and quickly burning in main combustion chamber 11. such as can control to inject the beginning of main combustion gas by main gas valve 21 according to the current loads of gas engine 1.First determining the injection persistent period according to current loads, described injection generally also can continue for some time after lighting a fire in precombustion chamber 15. and igniting in precombustion chamber 15, main injection combustion gas being injected in main combustion chamber 11 starts can be separate such as by engine control system control with the persistent period.
By controlled main gas valve 21, the supply of main combustion gas can also be matched with current load condition and combustion gas characteristic, the most such as, accurately measure further through control unit of engine ECU.The most rapid load variations quickly can be reacted.
nullAs mentioned above，Mechanical type pressure reduction preferably by the pre-control being configured to differential plunger handles valve 25 to inject main combustion gas. and the back side (surface A 3) of the second plunger 32 is connected with the supply pressure of the igniter fuel of electronics prechamber valve 18 with spring cavity 38 by blow-by tube 39 in a preferred embodiment. and the air pressure of main combustion gas acts on the plunger surface A1 of differential plunger within the of short duration period that main gas valve 21 is opened、A2，Wherein，The air pressure of main combustion gas is chosen as so more than the pressure of the igniter fuel for precombustion chamber 15，Thus ensureing that mechanical valve 25 is reliably opened under all situations of the compression pressure mating reaction (acting on plunger 31 by injection channel 37) in the main combustion chamber 11 of the pressure application surface acting on the first plunger 31. so only by the pressure of the igniter fuel adjusting main combustion gas and precombustion chamber 15，It is ensured that the function of mechanical valve 25.
The pressure of main combustion gas certainly have to be larger than main combustion gas and injects the expection compression pressure in moment. and main combustion gas being injected in main combustion chamber 11 during burning, the pressure of the most main combustion gas the most also have to be larger than intended combustion pressure.Main combustion gas is injected into the persistent period in main combustion chamber 11 be should also be as at most long as the time of oxygen for combustion existence certainly.
Owing to mixture is thin and actuating pressure in precombustion chamber 15 is the highest, high power spark ignition may be needed, ignition energy needed for could introducing and ignition voltage, the such as modulating capacitor igniting described in DE102008006304A1, or corona, plasma or laser ignition, or similar igniting form. the most such as with WO2013/045288A1 described in as, monitor the igniting in precombustion chamber 15 by monitoring ion current.
The particularly advantageous embodiment of another kind of the present invention is by igniter fuel multi-injection to precombustion chamber 15.Here, first a certain amount of igniter fuel is injected in precombustion chamber 15, with this formed the thinnest, certainly will not the igniter fuel/air mixture of premature ignition.Then continued to spray into igniter fuel before soon igniting, it makes the such enriching of mixture in precombustion chamber 15 China and foreign countries source igniter 16 next-door neighbour's surrounding, make available external source igniter 16, the most also reliable ignition can be realized with few ignition energy. the most additionally supply temperature igniter fuel more significantly lower than the compressed mixture in precombustion chamber 15, additionally cooling igniting fuel/air mixture, if thus reduced because adding and spraying into igniter fuel and cause the danger of undesirable spontaneous combustion. use such as liquefied gas (such as natural gas) as igniter fuel, such as in the ultralow temperature liquid phase of about-160 DEG C, it pressurizeed and make it evaporate before ejecting, the produced same temperature of gas is the lowest, this method can cause the mixture temperature in precombustion chamber 15 substantially reduce.
Preferably but not necessarily, use identical medium as main combustion gas and igniter fuel, such as natural gas, especially liquefied natural gas, different pressure may be needed only to for the main combustion gas for the igniter fuel of precombustion chamber 15 with for main combustion chamber 11.
nullFigure 10 show a kind of possible population structure. controlled gas engine 1 (being depicted with arrows) by control unit of engine ECU. and utilize control unit of engine ECU especially to control prechamber valve 18 and main gas valve 21，Pressure p 1 especially in accordance with main combustion gas and igniter fuel、The current load conditions (moment of torsion on the such as output shaft of gas engine 1 and/or rotating speed) of p2 and gas engine is if controlling corresponding injection and starting to terminate with corresponding injection. and prechamber valve 18 is connected with the igniter fuel memorizer 70 for igniter fuel by suitable gas pipeline. and main gas valve 21 is connected with the main combustion gas memorizer 71 for main combustion gas by suitable gas pipeline. and the medium of main combustion gas and igniter fuel is identical，Then a memorizer can also be set only to both. control unit of engine ECU also can control external source igniter 16，Also time of ignition and/or ignition energy can be controlled by ignition control unit 72 time especially necessary. perhaps can also adjust main combustion gas and/or the pressure p 1 of igniter fuel by control unit of engine ECU、p2，The such as the most known pressure-regulating device by being shown without in figure adjusts.

Claims (17)

  1. null1. for gas supply and the igniter of gas engine (1)，Described gas engine has combustion chamber burner (12)，Some injection channels (37) for main combustion gas it are provided with in described combustion chamber burner，And injection channel (37) is connected with the main gaspipe (24) for main combustion gas，And in combustion chamber burner (12), it is additionally provided with some passage of flames (52) for the burning gases of heat，And passage of flame (52) is connected with the precombustion chamber (15) in gas supply and igniter (10)，Wherein，Igniter fuel supply pipe (17) is passed in precombustion chamber (15)，And in igniter fuel supply pipe (17), it is provided with prechamber valve (18)，Wherein，Described prechamber valve (18) is configured to electrically operated、Electronically controlled valve，It is characterized in that，Main gas valve (21) it is provided with in main gaspipe (24)，Described main gas valve is configured to electrically operated、Electronically controlled valve，And between the main gaspipe (24) with the main gas valve (21) being provided with and injection channel (37), it is provided with mechanical type pressure reduction handles valve (25)，Described mechanical type pressure reduction handles the valve Stress control by main combustion gas，And close or block injection channel (37).
  2. Gas supply the most according to claim 1 and igniter, it is characterized in that, arranging to distribution the passage of flame (52) of multiple burning gases for heat on the periphery of combustion chamber burner (12), described passage of flame is connected with precombustion chamber (15).
  3. Gas supply the most according to claim 1 and 2 and igniter, it is characterised in that injection channel (37) and passage of flame (52) circumferentially direction are alternately arranged side by side.
  4. 4. according to the gas supply described in Claims 2 or 3 and igniter, it is characterised in that the entrance area of injection channel (37) and passage of flame (52) is substantially provided in the same axial position of combustion chamber burner (12).
  5. 5. according to the gas supply according to any one of claim 2 to 4 and igniter, it is characterised in that the entrance area of injection channel (37) and passage of flame (52) is radially directed.
  6. Gas supply the most according to claim 1 and igniter, it is characterized in that, the precombustion chamber groove (50) of annular it is provided with in gas supply and igniter (10), described precombustion chamber groove is connected with precombustion chamber (15) by precombustion chamber pipeline (51), and passage of flame (52) is passed in described precombustion chamber groove.
  7. Gas supply the most according to claim 1 and igniter, it is characterized in that, mechanical valve (25) is configured to valve tappet (30), described valve tappet has the first plunger (31) on an axial end portion and has second plunger (32) axially spaced with the first plunger (31), wherein, described first plunger (31) is connected with the second plunger (32) by bar (33), and on the first plunger (31), it is provided with plunger seal face (36), described plunger seal face sealingly engages effect with the valve sealing surface (41) in gas supply and igniter (10), and constitute between the first plunger (31) and the second plunger (32) and have the control chamber (46) being connected with main gaspipe (24).
  8. Gas supply the most according to claim 7 and igniter, it is characterized in that, second plunger (32) is arranged in the control recess (42) of gas supply and igniter (10), wherein, the side face of the second plunger (32) sealingly engages effect with controlling recess (42).
  9. Gas supply the most according to claim 8 and igniter, it is characterized in that, latch (34) is axially adjacent to the second plunger (32), described latch and backstop (43) mating reaction in gas supply and igniter (10).
  10. Gas supply the most according to claim 9 and igniter, it is characterised in that between backstop (43) and the second plunger (32), be provided with valve spring (45) around latch (34).
  11. 11. gas supply according to claim 7 and igniters, it is characterized in that, second plunger (32) is arranged in valve chest (53), constituting in described valve chest and have valve backstop (56), described valve backstop sealingly engages effect with the end face (55) of the second plunger (32).
  12. 12. gas supply according to claim 11 and igniters, it is characterised in that be provided with valve spring (45) between the end face (55) and valve chest (53) of the second plunger (32).
  13. 13. gas supply according to claim 7 and igniters, it is characterised in that be provided with a number of potted component (35) on the side face of the second plunger (32).
  14. 14. according to the gas supply according to any one of claim 7 to 13 and igniter, it is characterized in that, control chamber (46) and the end closed by the second plunger (32) is passed through blow-by tube (39) controlling deviating from of recess (42).
  15. 15. gas supply according to claim 14 and igniters, it is characterised in that blow-by tube (39) is connected with igniter fuel supply pipe.
  16. 16. application in gas engine according to the gas supply according to any one of claim 1 to 15 and igniter, in the main combustion chamber (11) of the cylinder (5) that the axial end portion of combustion chamber burner (12) extend into gas engine (1).
  17. null17. for the method running gas engine，In the process，During compression stroke in the cylinder (5) of gas engine (1) compressed air or air/exhaust-gas mixture，And the air of compression is pressed in precombustion chamber (15)，It is fed to igniter fuel in precombustion chamber (15) form air/igniter fuel mixture，By in the main combustion chamber (11) of main gas supply to cylinder (5) before compression stroke terminates，And the air in precombustion chamber (15)/igniter fuel mixture is lighted，Thus the burning gases of heat are flowed into main combustion chamber (11) from precombustion chamber (15)，And there the main combustion gas injected is lighted，It is characterized in that，Again igniter fuel is sent in precombustion chamber (15) before air in lighting precombustion chamber (15)/igniter fuel mixture，So as the air in enriching precombustion chamber (15)/igniter fuel mixture.
CN201610141402.2A 2015-01-07 2016-01-07 The gas supply and igniter of gas engine Active CN105822460B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50006/2015A AT516250B1 (en) 2015-01-07 2015-01-07 Fuel gas supply and ignition device for a gas engine
ATA50006/2015 2015-01-07

Publications (2)

Publication Number Publication Date
CN105822460A true CN105822460A (en) 2016-08-03
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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107420228A (en) * 2017-06-28 2017-12-01 哈尔滨工程大学 A kind of outer guiding fuel gas injection valve of bypass type axial admission
CN108005825A (en) * 2016-10-27 2018-05-08 福特环球技术公司 Fuel injector with three-level
CN110107392A (en) * 2018-02-01 2019-08-09 Ge延巴赫两合无限公司 Pre-chamber arrangement for combustion engine
CN111894775A (en) * 2020-08-26 2020-11-06 中船动力研究院有限公司 Supercharged fluid injection device and internal combustion engine
CN113302122A (en) * 2019-01-08 2021-08-24 三菱重工业株式会社 Marine boiler and method for modifying marine boiler
CN115263527A (en) * 2022-07-07 2022-11-01 广西玉柴机器股份有限公司 Ignition device with active intake prechamber
CN115387898A (en) * 2022-08-31 2022-11-25 东风商用车有限公司 Internal combustion engine and ignition control method thereof
CN115434820A (en) * 2021-07-27 2022-12-06 淄柴机器有限公司 Cylinder cover of oil-gas dual-fuel marine engine and engine with same

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT516618B1 (en) * 2015-02-27 2016-07-15 Ge Jenbacher Gmbh & Co Og cylinder head
CN108026827B (en) * 2015-06-30 2019-12-31 康明斯公司 Nozzle combustion shroud
EP3181854A1 (en) * 2015-12-14 2017-06-21 Caterpillar Energy Solutions GmbH Pre-chamber of internal combustion engine
EP3267008A1 (en) * 2016-07-06 2018-01-10 Mahle Powertrain LLC Method for starting an internal combustion engine
JP6625950B2 (en) * 2016-09-05 2019-12-25 ヤンマー株式会社 Engine equipment
GB2554368B (en) * 2016-09-22 2020-06-03 Delphi Tech Ip Ltd Dual fuel injector nozzle with an anti-leakage feature
SE543937C2 (en) * 2018-10-11 2021-09-28 Scania Cv Ab A pre-chamber arrangement and a gas engine for increased combustion efficiency
DE102019109603A1 (en) * 2019-04-11 2020-10-15 Man Truck & Bus Se Method for operating an internal combustion engine
DE102019006486A1 (en) * 2019-09-12 2021-03-18 Man Truck & Bus Se Method for operating an internal combustion engine, having a main combustion chamber and an antechamber, with gas fuel.
DK180798B1 (en) * 2020-07-15 2022-04-01 Man Energy Solutions Filial Af Man Energy Solutions Se Tyskland Internal combustion engine
CN113417733B (en) * 2021-06-28 2022-09-13 大连理工大学 Fuel-air separation active control type ignition chamber system
US11549441B1 (en) 2021-10-12 2023-01-10 Collins Engine Nozzles, Inc. Fuel injectors with torch ignitors
DE102023115185A1 (en) 2023-06-12 2023-08-31 Daimler Truck AG Injection system for a gas engine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050274828A1 (en) * 2004-06-11 2005-12-15 Michael Kurz Fuel injector with multi-part injection valve member and with pressure booster
US20120125279A1 (en) * 2010-11-23 2012-05-24 Woodward Governor, Inc. Pre-chamber spark plug with tubular electrode and method of manufacturing same
CN102713235A (en) * 2010-01-19 2012-10-03 罗伯特·博世有限公司 Method for controlling the temperature of an injector of an injection system for injecting fuel into the combustion chamber of an internal combustion engine
CN103814208A (en) * 2011-06-14 2014-05-21 西港能源有限公司 Dual fuel injection valve
CN103925119A (en) * 2013-01-11 2014-07-16 卡特彼勒公司 Gaseous common rail fuel system and high compression ratio engine using same

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2799255A (en) * 1955-03-14 1957-07-16 Cooper Bessemer Corp Gas engine
FI88333C (en) * 1991-06-25 1993-04-26 Waertsilae Diesel Int FOERBAETTRAT INSPRUTNINGSVENTILARRANGEMANG FOER BRAENSLE
US5251594A (en) * 1991-12-31 1993-10-12 Leonard Meyer Nutating internal combustion engine
FI101169B (en) * 1995-12-08 1998-04-30 Waertsilae Nsd Oy Ab Injection valve arrangement for an internal combustion engine
DE19622945A1 (en) * 1996-06-07 1997-12-11 Wtz Fuer Motoren Und Maschinen Operation method for IC engine for gaseous fuel
JPH1026058A (en) * 1996-07-09 1998-01-27 Mitsubishi Heavy Ind Ltd Two fluid injection valve of internal combustion engine
US7401603B1 (en) * 2007-02-02 2008-07-22 Altronic, Inc. High tension capacitive discharge ignition with reinforcing triggering pulses
AT505666B1 (en) * 2007-08-20 2009-03-15 Bosch Gmbh Robert METHOD AND DEVICE FOR INJECTING FUEL INTO THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
FI123513B (en) * 2010-12-02 2013-06-14 Waertsilae Finland Oy Fuel supply unit, method for operating it and combustion engine
US8978632B2 (en) * 2011-09-28 2015-03-17 Hoerbiger Kompressortechnik Holding Gmbh Ion sensing method for capacitive discharge ignition
JP2013217335A (en) * 2012-04-11 2013-10-24 Mitsubishi Heavy Ind Ltd 2-cycle gas engine
GB201309124D0 (en) * 2013-05-21 2013-07-03 Delphi Tech Holding Sarl Fuel Injector
DE102013009413B4 (en) * 2013-06-05 2024-06-20 Man Energy Solutions Se Ignition device for igniting a gas mixture of a gas-powered internal combustion engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050274828A1 (en) * 2004-06-11 2005-12-15 Michael Kurz Fuel injector with multi-part injection valve member and with pressure booster
CN102713235A (en) * 2010-01-19 2012-10-03 罗伯特·博世有限公司 Method for controlling the temperature of an injector of an injection system for injecting fuel into the combustion chamber of an internal combustion engine
US20120125279A1 (en) * 2010-11-23 2012-05-24 Woodward Governor, Inc. Pre-chamber spark plug with tubular electrode and method of manufacturing same
CN103814208A (en) * 2011-06-14 2014-05-21 西港能源有限公司 Dual fuel injection valve
CN103925119A (en) * 2013-01-11 2014-07-16 卡特彼勒公司 Gaseous common rail fuel system and high compression ratio engine using same

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108005825A (en) * 2016-10-27 2018-05-08 福特环球技术公司 Fuel injector with three-level
CN108005825B (en) * 2016-10-27 2022-06-14 福特环球技术公司 Fuel injector with three stages
CN107420228A (en) * 2017-06-28 2017-12-01 哈尔滨工程大学 A kind of outer guiding fuel gas injection valve of bypass type axial admission
CN110107392A (en) * 2018-02-01 2019-08-09 Ge延巴赫两合无限公司 Pre-chamber arrangement for combustion engine
CN110107392B (en) * 2018-02-01 2022-11-08 Ge延巴赫两合无限公司 Pre-chamber arrangement for a combustion engine
CN113302122A (en) * 2019-01-08 2021-08-24 三菱重工业株式会社 Marine boiler and method for modifying marine boiler
CN113302122B (en) * 2019-01-08 2024-04-12 三菱重工船用机械株式会社 Boiler for ship and method for modifying boiler for ship
CN111894775A (en) * 2020-08-26 2020-11-06 中船动力研究院有限公司 Supercharged fluid injection device and internal combustion engine
CN111894775B (en) * 2020-08-26 2024-04-23 中船动力研究院有限公司 Supercharged fluid injection device and internal combustion engine
CN115434820A (en) * 2021-07-27 2022-12-06 淄柴机器有限公司 Cylinder cover of oil-gas dual-fuel marine engine and engine with same
CN115434820B (en) * 2021-07-27 2024-06-21 淄柴机器有限公司 Cylinder cover of oil-gas dual-fuel marine engine and engine with cylinder cover
CN115263527A (en) * 2022-07-07 2022-11-01 广西玉柴机器股份有限公司 Ignition device with active intake prechamber
CN115387898B (en) * 2022-08-31 2023-12-22 东风商用车有限公司 Internal combustion engine and ignition control method thereof
CN115387898A (en) * 2022-08-31 2022-11-25 东风商用车有限公司 Internal combustion engine and ignition control method thereof

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AT516250B1 (en) 2016-04-15
US20160195003A1 (en) 2016-07-07
CN105822460B (en) 2019-10-01
AT516250A4 (en) 2016-04-15
EP3043048B1 (en) 2018-09-19
EP3043048A1 (en) 2016-07-13

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